Machine tool transmission and control



April 1 F. A. PARSONS' MACBI'NE TOOL TRANSMISSION AND CONTROL Filed Oct.4, 1935 8 Sheets-Sheet 1 q INVENTOR 2 6 WW ATT-ORNEY April 9 F. A.PARSONS 2,077,435

MACHINE TOOL TRANSMISSION AND CONTROL Filed Oct. 4, 1935 s Sheets-Sheet2 i Ill AINVENTOR- 1 ATTORNEY j F. A. PARSONS 2,077,435

April 20, 1937.

MACHINE TOOL TRANSMISSIQN AND CONTROL 8 Sheets-Sheet 3 Filed Oct. 4,1955 ATTORNEY F. A. PARSONS MACHINE TOOL TRANSMISSION AND CONTROL FiledOct. 4, 1935 8 Shets-Sheet 4 a INVENTOR AfroRNEv .'April 20,1931

April 20, 1937. F. A. PARsoNs MACHINE TOOL TRANSMISSION AND CONTROLFiled Oct. 4, 19:55

8 Sheets-Sheet 5 April 20, 1937. 1 F, PARSONS 2,077,435

MACHINE TOO L TRANSMISSION AND CONTROL Filed Oct. 4, 1955 s Sheets-Sheete n INVENTOR r w/a ATTORNEY April 20, 1937.

F. A. PARSONS MACHINE TOOL TRANSMISSION AND CONTROL Filed Oct. 4, 1935III IE 8 Sheets-Sheet 7 ATTORNEY Filed Octf 4, 1955 8 Sheets-Sheet 8INVENTOR' '3 W 4 i ArroRuiY Patented Apr. 20, 1937 PATENT OFFICE MACHINE'roor. TRANSMISSION'AND CONTROL Fred A. Parsons, Milwaukee, Wis.,assignor to Kearney & Trecker Corporation, West Allis, Wis., acorporation of Wisconsin Application October 4, 1935, Serial No. 43,488

38 Claims.

This invention relates to machine tools and more particularly totransmission and control mechanism therefor, especially for millingmachines.

An object of the invention is to provide an improved transmissionmechanism, particularly of the hydraulic type, and controls therefor,which may be used for either hand or automatic operation of a machinetool, and for machine movements involving both hand and automaticcontrols, particularly for a milling machine.

Further objects relate to improved control mechanism for the automaticreversal of machine movements without use of lost motion mechanicalsnap-over devices, whereby to obtain certain advantages to be had in theabsence of such devices and to avoid certain objectionable featuresattendant on their use.

A further object is to provide improved automatic reverse means foreffecting reversal at a predetermined point of forward movement.

Further objects relate to an improved transmission and control in whichboth the direction and the alternative selection'of feed or quicktraverse rates are determined by separate and individually operablecontrollers, but other control means may operatefor the simultaneouscontrol of rate and direction in such manner that, for instance, thereverse simultaneously effects a quick traverse rate irrespective of therate of forward movement, particularly for milling machines, andespecially for hydraulically actuated machines.

A further purpose is to provide an improved control for the main clutchof a milling machine, and to interconnect the clutch control in animproved manner with other transmission and control mechanism of themachine, and especially with control mechanism such as is indicated inthe last pereceding paragraph.

A further purpose is to provide an improved control mechanism at leastin part hydraulically operated for some or all of the control purposespreviously mentioned and especially where some of the control mechanismof the machine is manuallyoperated; and particularly for a millingmachine.

A further purpose is to provide a transmission and control mechanismeffective for some or all of the improved results obtained by themechanism shown in aco-pending application, Serial No. 36,766, filedAugust 19, 1935, but in a form particularly adapted for hydraulicallyactuated machine tools.

A further purpose is generally to simplify and improve the constructionand operation of machine tools, and particularly of milling machines,and still other purposes will be apparent from the accompanyingdescription and claims.

Certain related inventions are shown and par- 5 ticularly claimed in theco-pending joint applications of Fred A. Parsons and Walter M. Pohl,Serial No. 65,744, filed February 26, 1936 and Serial No. 109,112, filedNovember 4, 1936, and also in the co-pending application to Joseph B. 10Armitage, Serial No. 86,559, filed June 22, 1936, and all rights to saidrelated inventions are particularly reserved.

The invention, except for certain aspects shown and claimed in saidco-pending application Serial 15 No. 36,766 for which all rights areparticularly reserved, consists in the construction and combination ofparts as herein'illustrated, described and claimed and in suchmodifications of the structures illustrated and described as are equiv-20 alent to the structure of the claims.

Like characters have been used to indicate the same parts throughoutthis specification, and in the drawings:

Fig. 1 is a right side elevation, partly in sec- 25 tion, of a millingmachine incorporating the invention.

Fig. 2 is a front elevation of the same machine. Fig. 3 is a sectionaldevelopment of certain drive mechanism of the machine in enlarged 30scale.

Fig. 4 is an enlarged partial vertical section taken approximately alongthe line 4-4 of Fig. 1 and enlarged.

Fig. 5 is an enlarged partial elevation, partly 35 in section of thefront portion of the machine as viewed from the left of Fig. 2.

Fig. 6 is a portion viewed approximately from the line 66 of Fig. 5, inreduced scale, and partly in section. 40

Fig. 7 is a section through a pump of the machine, taken approximatelyalong line 'l---! of Fig. 6, and enlarged.

Fig. 8 is a semi-diagrammatic development of certain transmission andcontrol mechanism of .the machine.

Fig. 9 is a partial front elevation of the machine, partially in sectionalong a line approxitaken approximately along line 44 of Fig. 1 andenlarged, the table portion being shown with a front cover removed.

Fig. 10 is an enlarged sectional view of a back pressure valve deviceused in the machine.

Fig. 11 is an enlarged sectional development taken approximately alongthe line llll of Fig. 2.

Fig. 12 is an enlarged partial section taken approximately along theline l2-|2 of Fig. 2.

Fig. 13 is a partial section taken approximately along the line l3-l3 ofFig. 9.

Fig. 14 is a semi-diagrammatic development corresponding to themechanism shown at the lower right of Fig. 8 but enlarged.

The machine here shown is amilling machine which includes a base orsupport i, Fig. 1, a ,work table or support 2 slidably guided on base I,a tool spindle or support 3 rotatably carried by a quill or support 4slidably keyed and guided for transverse adjustment together withspindle 3 in a carrier or support 5.- The carrier 5 is guided for bodilyvertical movement together with quill 4 and spindle 3 between sidemembers 6, i, Fig. 2, which are rigidly fixed on bed I and fixedtogether at the top by a member 8.

The guides for the various members may be of any suitable form andtherefore are not shown 'in detail. For the carrier 5 and quill 4 thereare provided suitable manual means for the movement thereof and suitableclamp means operative in their several positions. Such moving andclamping means being old are not here shown.

Transmission mechanism for rotation of spindle 3 includes a primarymotion source such as an electric motor 9, Fig. 1, carried by base I,and having a drive shaft l8 carrying a pulley II, which drives a pulleyI2, Fig, 3, through belt means l3. Pulley I2 is fixed on a shaft l4 anddrives a co-axial shaft l5 through a clutch generally denoted by thenumeral l6, the clutch including an outer member l1, an inner member l8,an adjustable abutment I9, a movable abutment 28, and a series offriction plates 2| alternately keyed to the outer and irmer clutchmembers and slidable into mutual friction engagement by a pivoted lever22, which is operated by suitable cam surfaces 23a on a clutch spool 23shiftable by a fork member 24 fixed on a shifter rod 25 which is movableby means later described.

Shaft l5, at an intermediate point, carries a spindle reverser,generally denoted by the numeral 26, Fig. 3, comprising meshed bevelgears 21, 28, 29, the gears 21, 29 having clutch teeth alternativelyengageable by complementary clutch teeth on a clutch member 38 slidablykeyed on shaft I5, and which may be shifted. by a manually operablelever 3|, Fig; 1, connected ,therewith by any suitable means, such asthe eccentric and fork there shown. The driven gear 28 is fixed on ashaft 32, Fig. 4, which drives a shaft 33 through a spindle ratechanger, generally denoted by the numeral 34, comprising a plurality ofdifferently diametered gear pairs such as the gears 35, 36 removably.ind interchangeably fixed on the different shafts. Shaft 33 drives avertical shaft 31 through bevel gears 38, 39. Shaft 31, Fig. 1, drivesspindle 3 through bevel gears 40, 4| extensible coupling 42, pinion 43and a gear 44 which is fixed on the spindle.

The spindle train is provided with a brake, generally denoted by thereference letter a, Fig. 3, which includes an inner member b, keyed toshaft IS, an outer member 0 fixed with base 1, a series of frictionplates d, alternately keyed to the outer and inner members, anadjustable abutment e, a movable abutment f, and a pivoted lever 11,which is moved to press the friction plates into mutual engagement by amember 11. fixed on the clutch spool 23.

The arrangement'of clutch l6 and brake a is such that in the onedirection of movement of shifter rod 25, Fig. 3, the clutch I6 isengaged to start spindle 3 and the other direction of movement of therod engages brake a.

The table 2 is alternatively driven through feed and quick traversetrains. The table feed train is driven from. motorQ through the mainclutch l6, Fig. 3, and the shaft l5, the shaft I 5 being extended todrive a sleeve 45, Figs. 5, 6, upon which is fixed a gear 46 meshingwith a pump drive gear 41, which drives a feed pump generally indicatedby the numeral 48, Fig. 7, housed within a unit 48, and fixed on bed I.Feed pump 43 may be any of several well known types, but as here shownincludes a plurality of pistons such as 50 bodily rotatable with amember5l which is driven from gear 41, and having more or less pumpingstroke accordingly as a member 52 is shifted to the right or left inFig. 6, the member 52 being continuously pressed by springs, not shown,in the one direction .and shifted in the other direction by the movementof a controlplunger or rod 53 Figs. 5, 6, by means of mechanism laterdescribed.

Fluid is led to and away from the pistons 50 of feed pump 48 throughchannels 54, 55 Fig. 7 in a pintle 56 upon which member 5| is mountedfor rotation, the respective channels being connected to receive fluidfrom a supply channel 51 diagrammatically indicated in Fig. 8, and todeliver fluid to'a channel 58 leading to table control mechanismgenerallydenoted bythe nu-' 61, 68 diagrammatically shown in Fig. 8,thepump having inlet and outlet ports respectively connected to receivefluid from a reservoir 69, Figs. 8, 9, in base I and to deliver fluid tothe feed pump supply channel 51 and also to a channel 18 which, like thefeed pump channel 56, is connected to the table control mechanism 58,Fig. 8 which will be later described.

Fluid from the pumps 48, 66, Fig. 8, may be delivered through thecontrol mechanism 59 to actuate a table motor, generally denoted by thenumeral H, through the channels 12 or 13, according to the position of areverser device including a reverser valve generally denoted by numeral14, Figs. 8, 9, and a feed or quick traverse rate selector including arate selector valve 15, Figs. 8, 9, the motor H including a cylinder 16,a piston 11, and a piston rod 18 which is fixed with table 2.

The various control connections of the table control mechanism 58, Fig.8, are as follows:

Feed pump fiuid from channel 58 passes to a port 18, Fig. 8, of reverservalve 14, which also includes ports 80, 8|, respectively, connected tothe channels 12, 13 leading to table motor II. In the central positionof reverser valve I4, as shown in Fig. 8, the fluid from port 19 cannotreach either port 80, 8|, and the table motor II and table 2 are lockedin position by the fluid on each' side of piston TI which then cannotescape past valve 14. In this central valve position the fluid from port18 is by-passed to an outlet channel 82 through ports 83, 84, to whichit passes through transverse holes 85, an axial bore 86 and thetransverse holes 81 or 88.

But if the reverser valve I4, Fig. 8, is shifted to right or left of theposition in Fig. 8, one or the other of the ports 88, 8|, which connectto channels I2 and I3 respectively, will receive fluid from port 19through one of the annular grooves 89, 98, and the other port 88, 8Iwill deliver fluid to one of the ports 83, 84 and outlet channel 82through the other annular groove 89, 98. Thus the motor II and table 2will be moved in the one direction or the other according to the Fig. 8,passes to a port 9| of valve I5. The valve has two positions, namely,the feed rate position shown in Fig. 8, in which the fluid from port 9Ipasses through an annular groove 92 to a port 93 to be used for variouspurposes, as later described, and another position, to the left of thatshown in Fig. 8, in which the fluid from port 9I passes through groove92 to a port 94, which communicates with the port I9 of the reverservalve I4. In the latercase the fluid delivered from channel I8 will be.added to that delivered from channel 58 to produce relatively fast tablemovement in either direction as controlled by reverser valve I4 aspreviously described.

The pumps 48, 66 are respectively provided with overload relief valves95, 96, Figs. 8, 9 which are of similar construction and therefore onlythe valve 96 will be described in detail. Valve 96 includes a plungermember 9! having anenlarged portion 98 acting as a piston andcontinuously urged by the fluid pressure of the pump applied through aport 99, the plunger movement being opposed by pressure of a spring I88,which may be adjusted by a threaded member IM to vary the pressure. Whenthe fluid pressure exceeds the maximum determined by the adjustment ofmember I8I the port 99 is opened to a channel I82 to permit fluid toreturn to reservoir 69.

The connections of the overload valves 95, 96 Fig. 8 to the pumps 48, 66and to the control valve 15 is such that when the table 2 is operatingat a feed rate the valve 95 controls the maxi mum table load capacity,while at quick traverse rate both the valves 95, 96 are connected toboth the pumps, and the load capacity is governed by whichever valve isadjusted for least pressure. Ordinarily this would be the valve 96.

It will be noted that, although both the fee pump and the quick traversepump are supplying fluid to table motor II during quick traversemovements, the quick traverse rate will remain the same, irrespective ofthe feed pump delivery setting, for the reason that the entire volumesupplied to the motor will be only that which is constantly deliveredby, the quick traverse pump. This is because the feed pump draws itsfluid from the outlet channel of the quick traverse pump as abovepointed out.

It may also be noted that there is no point inthe back pressure deviceshown in a co-pendingi application Serial No. 32,541 filed July 22,1935and therefore will not be described in detail. It includes a throttleplunger I86 spring urged in a direction to close throttle openings suchas I81, and urged in the other direction by fluid pressure opposing thespring pressure and derived through a channel I88 from the channel 94,which as previously explained leads to the forward or inlet side ofmotor II in eitherdirection of motor operation. Back pressure device I83also in cludes a restricted passage I89 supplementing the effect ofthrottle plunger I86, and a piston means II 8 operating in a liquidfilled chamber III to prevent axial vibration or chatter of plunger I86.The effect of device I83 is to maintain suiflcient back pressure on themotor II to prevent overrun under all conditions of machine operationand particularly when the cutter tends to set up a negative pressure orvacuum in the forward or motor supply channel, and to automaticallyreduce the back pressure as the pressure in forward channel 94 increasesand vice-versa, whereby to avoid power waste, heating, and otherundesirable results of a constantly high back pressure.

Feed pump 48, Fig. 8, is manually adjustable to change the feed rate bymechanism as'follows: A manually operable member II2, Figs. 2, 5, 11 isconnected for movement of the pump control plunger 53, previouslydescribed, through a shaft II3, pinion II4, an intermediate gear II5, agear II6, shaft III, a coupling II8, a shaft H9 and an eccentric cammember I28 which operates against the exposed end of the plunger 53. Asthe member I I2 is turned in the one or the other direction plunger 53,which is spring pressed together with member 52 as previously explained,follows the contour of cam member I28 thus altering the stroke of thefeed pump pistons. Associated with member H2 is an indicating deviceconsisting of a graduated dial I2I movable against an indicator I22which indicates on the dial the rate resulting from the variouspositions of the adjusting means.

The reverser and selector valves I4, I5, are

each movable from a lever I23, Figs. 2, 12. Lever I23 when oscillated toright or left in Fig. 12 shifts selector valve 15, Fig. 8, through apivot I24 carried by a sleeve I25, an arm I26 engaging a rod I21, a pinI28, Figs. 9, 12, a lever I29, a shaft I38, another lever I3I, and a pinI32 engaging a member I33 flxed on a shifter rod I34, Figs. 8, 9,

the shifter rod I34 being co-axial with the valve I5, and coupledtherewith by a pin I35.

Lever I23, when oscillated to right or left in I Fig. 2 shifts reverservalve I4, Fig. 8, through sleeve I25, Fig. 12, a lever I36, a pin I31and a member I38 fixed on a shifter rod I39, Figs. 8, 12, which forconvenience is made in two parts I39a, I391), joined togethenandco-axialwith valve I4 to which the shifterrod is coupled by a pin I48.

For dog operation of the-'reverser'valve I4, Fig. 8 there is provided atrip member I M, Fig. 9, having oppositely extended dog abutmentportions I 4Ia, I4Ib fixed on a sleeve I42, and alternatively rotatableinto the path of movement of table dogs such as I43, I44. A lever I45Figs. 9, 13, 14 fixed on sleeve I42 carries a pin I46 engaging a slot-I4| in the shifter rod I39 which is connected to reverser valve I4 aspreviously de-' scribed.

When reverser valve 14 is in central or table stop position both theabutment members I4Ia, I4 Ib are withdrawn out of the path of dogmovement but when the valve is shifted to establish ment is swungforward into the path of dog movement, and will be contacted by the dogduring table movement to return the valve to central position, therebystopping the table.

For dog operation of feed and quick traverse selector valve 15, Fig. 8,there is provided a trip post I48, Figs. 9, 13, having a plurality ofdog abutment members I49, I50, the post being slidably keyed in thesleeve I42 to oscillate with the sleeve but having individual verticalmovement. When the sleeve I42 is in the position corresponding tothecentral or table stop position of reverser valve 14, both abutmentsI49, I50 are withdrawn out of dog contacting position, but during tablemovement one or the other of the abutments is swung forward and may thenbe contacted by dogs such as dogs II, I52 respectively adapted forupward and downward post movement. A pin I53 is fixed in the arm I54 ofa pivoted lever I55 and engages a suitable groove in the lower end ofpost I48, the lever I 55 having another arm I56 carrying a pin I51 whichengages a slot I58 in the shifter rod I34, which is connected toselector valve 15 as previously described. A given direction of tablemovement always moves the same abutment I49 or I50 into dog contactingposition and withdraws the other, and since the abutments are ondifferent levels any number of dogs such as I5I, I52 may be operative ineither direction of table movement to change from feed to quick traverserate, or vice-versa, at desired points without interference withsimilarly operative dogs for the other direction of table movement.Suitably spaced T slots I59, I60, Fig. 9 are provided for the upper andlower series of dogs.

Clutch I5 and brake a, Fig. 3, are shifted by the a 4 such as I64. PumpI63 may be of any suitable type, in this case comprising encased gearsI65, I65a driven from shaft 62, the pump having inlet and outlet portssuitably arranged, receiving fluid from a reservoir in base I,diagrammatically indicated at I61, Fig. 3, through a strainer I68 and aconnecting channel I69, and delivering fluid to valve means I64 througha channel I10.

The valve means I64, Fig. 3 provides a port "I supplied with fluid fromchannel I10, and the ports I12, I13 respectively connected by channelsI14, I15 with the opposite ends of piston I62.

A valve plunger I16 is continuously urged in one direction by a springI11 and may be urged in the other direction by fluid pressure derivedthrough a channel I18 as later described. When member I16 is in' itsspring urged position, as indicated in Fig. 3, the supply channel Icommunicates with port I13 through a valve groove I19 and the pistonI62is then urged ina direction to disengage clutch I5 and to engagebrake a, the fluid from the opposite end of piston I62 being forced outthrough channel I14, port I12, a valve groove I80 and a drain channelI8I which delivers fluid back to reservoir I61. v

Butwhen the channel I18 Fig. 3 is connected to a source of fluidpressure, as later described, the valve plunger I16 is shifteddownwardly in Fig. 3, and fluid from channel I10 then reaches the otherside of piston I62 through the valve groove I80 port I12 and channelI14, waste fluid passing from the channel I througha drain channel I82to permit the piston I62 to move in the direc- .tion to engage clutchI5. Pump I63 is also used for lubricating the machine as will be laterdescribed.

The control of' fluid pressure in channel I18, Fig. 3, for the shiftingof clutch I5 and brake a is primarily effected from a hand lever I 83,Figs. 2, 12, which has two positions normally respectively effective toshift piston I62 and shifter rod 25, Fig. 3, to clutch engaged and tobrake engaged positions. The control effect of hand lever I83 may,however be modified by shifting another hand lever I84, Figs. 2, 12. Inone position of the lever I84 the control effect of lever I83 is thenormal effect just described. In the other position of lever I84, theclutch engaged position of lever I83 is effective to engage the clutchI5 only when selector vave 15, Fig. 8, is in feed position, and when thevalve is in its quick traverse position the clutch I5 is disengaged andbrake a is engaged to stop spindle rotation. The means whereby thesecontrol effects are obtained is as follows:

Pressure fluid for the channel I18, Fig. 3, which controls the clutch I5and brake a, as previously explained, is supplied through channels laterdescribed froma channel I85, Fig. 8, which also supplies other controlmechanism as later pointed out. The supply of fluid to channel I85 isderived from port 93 of selector valve 15, which in the feed position ofthevalve, as shown in Fig. 8, is suppl'ed with fluid from quick traversepump 66 through port 9I and valve groove 92. In the quick traverseposition of valve 15, tothe left of the position shown in Fig. 8, theport 93 and channel I85 receive fluid from the motor outlet channel 82,through a valve groove I86. In either case the fluid pressure in channelI85 is controlled by arelief valve generally denoted by the numeral I81,Fig. 8, which communicates with channel I85 and port 93 through channelI88, and is of a construction similar to that of relief valves 95, 96previously, described. The connection of the relief valve I81 to thevalve port 93 also provides a constant pressure outlet for the fluidfrom motor 1I during quick traverse movements, since the fluid is thenunder no necessity to pass through the back pressure device I03previously described.

Fluid from channel I85 passes to a port I89 of a valve I90 Figs. 8, 14through a channel I9I the valve I90 being operably connected to the handlever I 83, Figs.'2, 12, by the means of a shaft I92, a lever I93, and apin I94 engaging a slot I 95 in a member I96.. In the position of valveI 90 as shown'in Figs. 8, 14, port I89 receives no fluid, but in theother position of valve I90, to the right of the position shown in Figs.8,-14, the fluid passes through a valve groove I91 to a port I98, andthence to channels I99 and 200 respectively leading to a port I of avalve 202 associated with the shifter rod I34, and to a port 203 of avalve 204, the latter valve being connected for operation from the handlever I84, Fig. 12, by the means of a shaft 205, and an eccentric pin206 engaging a slot 201 in a member 208, Figs. 8, 12, which is fixed onthe extended stem of valve 204.

The manner of delivery of fluid to the channel I18, Fig. 3, whichcontrols actuation of clutch shifter piston I62 and rod 25, aspreviously described, depends upon the position of valve 204,

Fig. 14. In the position of the valve 204 there shown the fluid may passfrom the channel 200 through a valve groove 209, a port 2 I 0 and thencethrough a channel 2II to a port 2I2 of the valve 202. In such case, ineither position of the selector shifter rod I34, fluid will be deliveredto a port 2 I3 of valve 202 through a valve groove 2I4 from the one orthe other of ports 20I or 2| 2, provided that the valve I90 is in aposition to the right of the position of Fig. 14. In the left handposition of valve I90, as shown in Fig. 14, no fluid will be deliveredto either port 20I, 2 I2 of valve 202, the fluid being unable to passfrom port I89 to port I98 of valve I90.

The port 2I3, Fig. 14, of valve 202 is continuously in communicationwith the clutch control channel I18, Fig. 3, through a channel 2I5connected to channel I'I8 through suitable piping, and therefore, withthe valve 204 in the position shown in Fig. 14, the control valve I64,Fig. 3 will be shifted to its position engaging clutch I5 whenever valveI90 is in its position to the right in Fig. 14 and irrespective of theposition of valve 202; and the control valve I64 will be shifted byspring I" to its position engaging brake a; whenever the valve I90 isshifted to the position shown in Fig. 14, the fluid pressure then beingcut off at valve I90, and the pressure immediately leaking out of thevarious connecting channels through a drain port 2I6, Fig. 14, which isexposed by the same left hand movement of valve I90 that cuts off thepressure supply from port I09.

It will therefore be apparent from previous explanation that, in theposition of valve 204 as shown in Fig. 14, the clutch I6 will be engagedwhenever valve I90 is -shifted to the right by hand lever I83 and thebrake a: will be engaged to stop the spindle 2 and feed pump 48 wheneverthe valve I90 and hand lever are shifted in the other direction.

But in the other position of valve 204, to the right of the positionshown in Fig. 14, no pressure fluid can reach the port 2 I2 of valve202, the port 2I0 then being closed from port 203, and in such casefluid can only pass to the channel I18 of control valve I64, Fig. 3,from port 20I of valve 202, and then only when shifter rod I 34 is inits feed position as shown in Fig. 14. In the other or quick traverseposition of shifter rod I34 the port 20I is closed and the fluidpressure in the channels 2I5, and I18 immediately leaks out through port2l3, valve groove 2, port 2I2, channel 2I I, and port 2I0 which is thenexposed to drain through the bore 2 I I. When this .occurs the valve I64immediately shifts to its brake engaging position.

Thus, in the one position of valve 204 the control of clutch I6 andbrake a will be from hand lever I83, which engages the clutch I6 orbrake a independently of the feed or quick traverse position' of shifterrod I 34, while in the other position of valve 204 the shifting ofselector shifter rod I34 to feed position engages clutch I6, providedlever I83 is in clutch engaged position, and shifting rod I34 to quicktraverse position engages the brake. These control effects areindependent of which of the several means here shown are used forshifting the selector valve I5 and its shifter rod I34.

It is to be noted that, irrespective of the position of shifter rod I34and the selector valve 15,

Fig. 8, the feed rate of table 2 cannot be effected unless t e spindleclutch I6 is engaged to rotate the spindle 3. This is because the feedpump 48 is driven through the clutch I6 as previously explained, andtherefore operates only when the clutch is engaged.

The reverser valve 14, Fig. 8, in addition to the dog control previouslydescribed for shifting it to its central or motion interruptingposition, may also be dog controlled for effecting automatic reversalfrom either direction of movement of table 2 to the other direction. Themeans for effecting such dog controlled reversal is as follows:

A pivoted lever 2I8, Figs. 9, 13, 14 has a plurality of arms 2I9, 220held normally central by spring plungers 22I, 222, which mayrespectively be depressed to turn the lever in the one or the otherdirection by the means of table dogs'223, 224

Fig. 9. Another lever arm 225 carries a pin 226, Figs. 13, 14, whichengages a suitable slot 221 in a sleeve 228 of a control valve generallydenoted by the numeral 229, Fig. 14, the sleeve being axially movable ineither direction from the normal central position shown in Fig. 14, bythe operationof the dogs 222, 223. An inner member 230 of valve 229 isformed integral withthe reverser shifter rod I39b, and is axiallyshiftable therewith.

In all positions'of the valve sleeve 228, Fig. 14,

In the normal central position of valve sleeve 2 228 the supply port 23Iis closedto both valve grooves 231, 24.I as shown in Fig. 14, but asshifter rod. I39 and valve member 230 are moved to rightor left, theport 23I is brought into communication with the one or the other valvegroove to deliver fluid to'that end of the piston which will urgemovement of the piston and of' shifter rod I39 in the same direction, atthe same time opening the other valve groove and therefore the other endof the piston 236 to a drain, the drain being provided in the one in-.

stance by a port 243 which drains through a slot 244, and the drainbeing provided in the other instance by a chamber 245 and a drainpassage 246.

In the operation just described, that is to say while sleeve 228 is inits normal or central position, the fluid pressure from valve 229 actsas detent means operating on piston 236 Fig. 14, to retain the rod I39and reverser valve 14, Fig. 8, in either of its table operatingpositions, and providing a central position of valve 229 in which thereverser valve I4 may be retained in central position for effecting atable stop, as previously explained. As long as sleeve 228 is permittedto remain in centralposition the operation of the dogs I43 and I44, tostop table movement as previously explained, would not be altered.

But if at the time of the operation of the dogs I43, I44, thecorresponding dog 223 or 224 is positioned to contact its plunger 22I or222, whereby to suitably shift sleeve 220 to right or left, in Fig. 14,as the case may be, then the valve member 230 will pass across theposition where port 23I is cut off from delivery of fluid to piston'236,and into a position where fluid pressure is urging the continuedmovement of piston 236 and shifter rod I39, before the dog I43 or I44has completed its trip effect and before table movement stops. In suchcase, the fluid pressure from valve 229, acting on piston 236 will urgereverser valve I4 across central position and into the reverse position,thereby effecting automatic reversal of the movement of table 2. At anearly point in the reverse move- .ment the dog operating on the plunger22I or 222 backs away from the plunger and the plunger springs forcesleeve 228 again to normal central position, the fluid still continuingto operate as a detent, as previously described, retaining reverservalve 14 and shifter rod I39 in whichever position it has been forced bythe automatic reversal just described.

It will also be obvious that, if the dogs 223, 224 and their connectionsto the sleeve 228 are such as to sumciently shift the sleeve, then itwill be unnecessary to use the dogs E43, I44 to efiect an initialmovement of the valve member 236', during reversal. In the presentinstance the dogs M3, I44 are unnecessary to effect automatic reversal;since the movement of the sleeve 228 from dogs 223, 224 is sumcient toreverse the pressure operating on piston 236 in either table operatingposition of the reverser shifter rod I39.

The described mechanism'is sumcient for automatic table reversal but thetime required for reversal will vary with the rate of table travel. Itis desirable at times, and particularly when table 2 is operating atslow-feed rates, to have the shifting of automatic reverser sleeve 228proceed at a relatively very fast rate, substantially independently ofthe rate of movement of the table, whereby to reduce the time requiredfor reversal. To effect this result, supplemental or additional meansare used for shifting sleeve 228, as follows:

A plunger 241, Figs. 8, 14 has enclosed ends whereby it may operate as apiston. At an intermediate point plunger 241 is provided with valvegrooves 248, 249 respectively connecting with the opposite plunger endsthrough axial bores 256', 25I and suitable radial bores such as 252,253. When the plunger 241 is shifted slighta ly in either direction theone or the other of grooves 248, 249 is brought into communication witha port 254 which is continuously supplied with fluid from the channel Ithrough the channel 233, the annular groove which constitutes port 234of valve 229, and a channel 255; and the plunger 241 will then bequickly shifted by the fluid pressure. Plunger 241 is connected formovement with the sleeve 228 by the means of a pin 256, Figs. 13, 14, inthe same lever arm 225 which actuates the sleeve, the pin engaging asuitable slot 251 in the plunger. The fluid admitted'to plunger 241tends to quickly fully shift it in the same direction as started by dogs223, 224 operating on the plungers 22I, 222 and as a result of thearrangement described both the plunger 241 and sleeve 228 will bequickly fully shifted almost immediately following the start of theshifting of sleeve 228 in either direction from dogs 223 or 224 aspreviously described.

When either piston end of plunger 241 is connected to shifter fluid fromthe port 254, the other piston end is connected to a drain, eitherthrough a direct drain hole 258 or through a drain hole 259 leading tothe chamber 245 and drain hole 246. After the completion of a reversemovement the fluid pressure is relieved on plunger 241, in a mannerlater described, to permit the return of the plunger and of sleeve 228and lever 2I8 to their normal central positions.

It is highly desirable in order to reduce operating time and for variousother reasons that at each automatic reversal of table 2 the reversemovement shall start at rapid traverse rate, but in many operations thework and cutter are engaged up to the instant of revers a d t i$ thennecessary that the change to quick traverse rate must not be effectedprior to the actual reversal. Means are provided to insure each of thesedesired results as follows:

When the reverser shifter rod I39, Fig. 14, has nearly completed itsshifting movement in either direction, the movement of piston 236 opensthe then the one or the other of ports 263, 264 is opened to receivefluid from groove 262, and from either of these ports the fluid passesthrough channel 265 to a channel 266 which communicates with one end ofa piston 261 fixed on the selector shifter rod I 34 of the feed andquick traverse selector valve 15. The result of the describedarrangement is to force the piston 261 and selector valve 15 to quicktraverse position, but only during automatic reversal, and then onlyafter the piston 236 and the reverser valve 14 have substantiallycompleted their reversing movement. The other end of piston 261 iscontinuously connected to a drain channel 268 and when the automaticreverse plunger 241 is in normal central position, that is to say at alltimes except during automatic reversal, the channel 266 is alsoconnected to drain through the port 263 and a valve groove 269 whichthen com-- municates with the drain channel 259, previously described.The arrangement of valve groove 269 relative to port 263 and drainchannel 259 is such that in either position of plunger 241 to effectautomatic reversal the last mentioned drain is cut off, but at all othertimes the piston 261 is drained at both ends as described and offers noresistance to movement of selector shifter rod I34 in either direction.

After the piston 261, Fig. 14, has been shifted to effect quick traverseduring automatic reversal as just described, the operation of automaticreversal is complete, and it is then desirable that the fluid pressureon plunger 241 be relieved, in order that the plunger 241 and sleeve 228may return to normal central position as soon as the reverse tablemovement has moved the dog 223 or- 224 away from its plunger 22I or 222.This is done bythe following means.

An annular groove 210 is provided in the piston 261, Fig. 14, and afterthe piston moves to its quick traverse position, as described, duringreversal, groove 210 completes a channel connection between the twopiston ends of plunger 241, the connection then including-a channel 21I,a channel 212 suitably connected therewith, the annular groove 216, andchannels 213, 214, 215. This connection equalizes the pressure on bothends of the plunger 241, which will then be moved to central normalposition by springs of plungers 22I, 222, as soon as the plungers arefree from the dogs. Since the. pressure is equalized on plunger 241whenever piston 261 and selector valve 15 are in quick traverseposition, the plunger 241 will not operate toeffect rapid shifting ofsleeve 228, as above described, at such times as the reverse is to beeffected from a forward table movement at quick traverse rate, but thislimitation is of no importance since the fast table movement duringforward quick traverse effects comparatively 'very rapid movement ofsleeve 228' directly from the movement of the table dog and withoutnecessity for the supplemental fluid operated shifting above described.

Still another automatic reverse means is provided, but operative onlyafter the table has been brought. against a positive stop. Such controlis desirable, for instance, when the work piece is to be maintainedstationary against the cutter for a period before reversal, andfollowing a forward feeding movement. The other reverse means includesstructure as follows:

Fixed on the table support or base I at the rear of table 2 is a unitgenerally denoted by the numeral 216, Figs. 5, 6, 8, having a main 'orbody member 216a. Unit 216 includes a shiftable control valve member211, which is normally held in central position, as in Fig. 8, by springmeans, as springs 218, 219, but which may be shifted axially in eitherdirection when contacted by right or left hand dogs such as 288,adjustably mounted on table 2.

Unit 216 also includes a piston plunger 28I, which is continuously urgedto the right in Fig. 8, by a spring 282, the pressure of which isadjustable by the means of an adjustable abutment member 283, threadedin the body 216a and locked in adjusted position 'by a nut 284.

When thevalve 211 is in normal central position pressure fluid from thesupply channel I85, Fig. 8, is continuously delivered to the right handor piston end of plunger 28I through a suitable connecting channelindicated by dotted line 285. Fig. 8, a channel 286, channel 281, anannular port channel 288, channel 289, a port 298. a va ve groove 29I, aport 292, and a channel 293. The result is to normally force the plunger28I to the left in Fig. 8, against the resistance of spring 282,

until the plunger strikes a' suitable abutment such as the rod 294 onthe end or the adjusting screw 283. At the same time the chamber orcylinder 295 in which the plunger operates is maintained filled withliquid.

But if valve 211 Fig. 8, is moved slightly in either direction, by dogssuch as 288, the pressure fluid is cut ofl' at the one or the other ofports 298, 292, and liquid under the pressure of spring 282 immediatelycommences to leak out of the chamber 295, there being suitable meansprovided preferably of constant area, and of material resistance, suchfor instance as a coil of tubing 298, having a relatively small bore andconnected to the chamber 295 by a channel 291 and tube 298. As theliquid leaks from chamber 295 the plunger 28I moves to the right in Fig.8, the rate of movement being determined by the pressure exerted byspring 282 as determined by the adjustment of screw 283.

Almost immediately following the cuttingroif of fluid supply to chamber295 as described, the adjustable contact member 299 carried by the dog288 will abut the end of the body portion 216 and positively arrest themovement of table 2,

which will then be maintained in this position by the fluid pressuredetermined by the overload relief valve 95.-

At a measured interval following the described positive stop of table 2the continued movement of plunger 28I to the right in Fig. 8 brings avalve groove388 into simultaneous communication with the port 288 and achannel 38I leading to a port 382 of valve 211, the length of theinterval being determined by the adjustment of member 283 to alter thespring pressure acting on the constant area of the leakage channel 296.In the normal central position of the valve 211 the port- 382 is closed,but when the valve is shifted as described in either direction-by dogs288, and following the shifting of plunger 28I, port 382 supplies fluidto one or the other of the ends of the reverser plunger 241, whereby toeffect automatic reversal as previously described. v 1

Thus, when table movement to the left in Fig. 8 has shifted valve 211 tothe left, channel 38I delivers fluid to the right end of plunger 241through a valve groove 383, a channel 384, a pipe 385 suitably connectedwith another pipe 386, and the channel 215. 'And when tablefmovement tothe right in Fig. 8 has shifted valve 211 to the right, channel 38Idelivers fluid to'the left end of plunger 241 through a valve groove381,- a channel 388, a. pipe 389 suitably connected with another pipe3I8 and the channel 2". The connections described are such that tablemovement in the opposite direction 'to the preceding movementimmediately results,' and always at quick traverse rate for reasonspreviously explained.

valve 211, following table reversal, the valve again assumes its normalcentral position and plunger 28I again is moved to the left in Fig. 8,the unit then being ready for another reversing effect.

Automatic control means are provided foradjusting feed pump 48., asfollows: An eccentric cam 3| I, Fig. 5, is fixed on a sleeve '3I2 foractuation of the pump adjusting plunger 53 in a manner similar to thecam I28 previously described, and is connected for movement from a cam3I3 adjustably fixed on table 2, Figs. 5, 6, through a cam follower 3I4adjustably fixed on a shaft 3I5, a segment lever 3| 6, also fixed onshaft 3I5, an idler gear 3I1, and a gear 3I8 fixed on the sleeve 3I2.The cam follower 3 is continuously urged against the cam M3 by a spring3I9 andthe pump adjusting cam 3| I thus forced to adjust the pump duringtable movement in accordance with the configuration of cam 3I3. Therange or ratio of feed rates thus obtained, and the table feed rate atany given position of table movement-is, there-- The pump I63, Fig. 3,which supplies fluid for operating clutch I6 and brake a, as previouslydescribed, is also used. for lubricating the, ma chine. The cylinder ofpiston I62 is provided with a port 32I which is opened to the pressurefluid actuating the piston but only after the piston has 4 completed itsmovement in either direction. This fluid is directed to any pointsrequiring lubrica tion through a channel 322 and a lubricant supply pipe323. For the lubricating supply there is provided a pressure controlvalve 324, comprising a spring pressed ball 325. the excess fluidpassingthrough a drain hole 326 to return to reservoir I81, as does also anyexcess or drain from the various parts lubricated from pipe 323. Thesystem shown provides a high pressure fluid supply for the, shifting ofthe clutch I5 and brake a, but limits the duration of high pressuretothe very brief interval while the piston I62 is being shifted, therebyavoiding power waste and heating of the fluid.

What is claimed is:

1. In a machine tool, the combination of a tool support and .a worksupport, a transmission forrelative movement of said supports includinga fluid supply source and a fluid operable motor,

' As soon as the dog 288 has moved away from rate selector meansshiftable to eflect actuation of said motor from said sourcealternatively at a feed rate or at a relatively fast quick traverserate, shiftable reverser means operative to change the direction ofmotor movement, and control means i for said transmission includingafirst controller for operation of said reverser means independently of achange in rate, a second controller operable for operation of saidselector means independently of a change in direction, and anothercontrol means for shifting said reverser means and dependentlysubstantially simultanesource and a fluid operable motor, selector meansshiftable for alternative actuation of said motor from said source at afeed rate or at a relatively fast quick traverse rate, shiftablereverser means operable for changing the direction eifect of said motor,a plurality of controllers each independently operable and respectivelyfor operation of said reverser means and for operation of said selectormeans whereby to independently effect a change of direction or of rate,and other control means operative for shifting said reverser means anddependently substantially simultaneously shifting said selector means.

3. In a machine tool, the combination of a tool support and a worksupport, a transmission for relative movement of said supports includinga pressure fluid supply source and a fluid operable motor, rate selectormeans shiftable to effect actuation of said motor alternatively at afeed rate or at a quick traverse rate, reverser means shiftable forchanging the direction of said motor,

a first manually operable controller for operation of said reversermeans independently of a change of rate, a second controller manuallyoperable for operation of said selector means independently of a changein direction, and dog controlled means for shifting said reverser meansand dependently substantially simultaneously shifting said selectormeans.

4. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a direction transverse to the axis of saidspindle, transmission mechanism for rotation of said spindle, atransmission for movement of said work support including a pressurefluid supply source and a fluid operable motor, selector valve meansshiftable for alternative actuation of said motor at a feed rate or at aquick traverse rate, reverser valve means shiftable for change in thedirection of said motor, a plurality of independently manually operablecontrollers respectively for the operation of said reverser means and ofsaid selector means whereby to independently effect a change ofdirection or of rate, and dog controlled means operative for shiftingsaid reverser valve means and dependently substantially simultaneouslyshifting said selector valve means.

5. In a machine tool, the combination of a tool support and a worksupport, a transmission for relative movement of said supports includinga pressure fluid supply source and a fluid operable motor, selectormeans shiftable for alternative actuation of said motor at feed or quicktraverse rates, reverser means operable to change the direction of saidmotor, a first manually operable controller for shifting saidreversermeans independently of a change in rate, a second controller I manuallyoperable for shifting said selector means independently of a change indirection, and a dog controlled means operative to shift said reversermeans out of one direction position to the other direction positionthereof and dependently substantially simultaneously shift said selectormeans to a position effecting motor movement at said quick traverserate.

' 6. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a direction transverse to the axis of saidspindle, transmission mechanism for'rotation of said spindle, atransmission for movement of said work support including a feed ratepump and a quick traverse rate pump, a motor connectible for operationfrom said pumps, a shiftable reverser valve means, selector valve meansshiftable for alternative actuation of said motor at the one or theother of said rates, a plurality of independently manually operablecontrollers respectively for the operation of said reverser valve meansand of said selector valve means whereby to independently effect achange of direction or of rate, and dog controlled means operative toshift said reverser valve means out of one direction position to theother direction position thereof and substantially simultaneously todependently operate said selector valve means to a position eiiectingmovement of said motor at said quick traverse rate.

7. In a machine tool, the combination of a tool support and a worksupport, a transmission for relative movement of said supports includinga feed rate pump, a quick traverse rate pump, a shiftable reverser valvemeans operative to change the direction of said support movement ateither of said rates, a selector valve means shiftable to eifcctmovement of said motor alternatively at the one or the other of saidrates, a

first manually operable controller for operation of said reverser valvemeans independently of a change of rate, a second controllerindependently manually operable for operation of said selector valvemeans independently of a change of direction, and a dog controlled meansoperative to shift said reverser valve means out 01 either directionposition thereof to the other direction position and substantiallysimultaneously dependently shift said selector valve means for effectingsaid motor movement at said quick traverse rate.

8. .In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a direction transverse to the axis of saidspindle, transmission mechanism for rotation of said spindle, a feedrate pump, a quick traverse rate pump, a fluid operable motorconnectible with said pumps and connected for movement of said worksupport, reverser valve means operative to change thedirection of saidmotor, selector valve means shiftable for alternative actuation of saidmotor at the one or the other of said rates, a plurality ofindependently manually operable controllers respectively for theoperation of said reverser valve means and of said selector valve means,and a dog controlled means operative to shift said reverser valve meansout of either direction position thereof to the other direction positionand substantially simultaneously to dependently shift said selectorvalve means to efiect movement of said motor at said quick traverserate.

9. In a machine tool, the combination of a tool support and a worksupport, a transmission for relative movement of said supports includ- I2,077,436 ing a pressure fluid supply source and a motor connectibletherewith, shiftable reverser means operative to change the direction ofmovement of said motor, selector means shiftable to effect said motormovement alternatively at feed or quick traverse rates, a plurality ofmanually operable controllers respectively for independently shiftingsaid reverser means and said selector means, a dog controlled means forshifting said reverser means and substantially simultaneouslydependently shifting said selector means, and

other control means including a plurality of dogoperable meansrespectively for independently shifting said reverser means and saidselector means. I

10. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a direction transverse to the axis of saidspindle, transmission mechanism for rotation of said spindle, a fluidoperable motor connected for movement of said support, a fluid supply.

source connectible for actuation of said motor,

, reverser means shiftable for motor movement alternatively'in the oneor the other direction,

selector means operable independently of said re-' shifting saidreverser means and said selector means.

11. In a machine tool, the combination of a tool support and a worksupport, a fluid operable motor connected for relative movement of saidsupports, a pressure fluid supply source connectible for actuation ofsaid motor at alternative feed or quick traverse rates, shiftablereverser means operative to change the direction of a said motor, aselector means shiftable to efiect the one or the other of said rates,'afirst manually operable controller for shifting said reverser means, asecond manually operable controller for shifting said selector means,said first and second controllers being selectively operable either forindependent or for substantially simultaneous operation, and dogcontrolled means invariably effective for shifting said reverser meansand substantially simultaneous shifting of said selector means to aposition efiecting said mo-' tor movement at said quick traverse rate.

12. Ina milling machine the combination of a rotatable tool spindle, awork support reciprocable in a direction transverse to the axis of saidspindle, transmission mechanism for rotation of said spindle, a fluidoperable motor connected for movement of said support, a fluid supplysource connectible for operation of said motor alternatively at feed orquick traverse rates, reverser valve means shiftable for connection ofsaid source and motor for motor movement alternatively in the one or theother direction, independently operable selector valve means shiftablefor connection of said source to actuate said motor at the one or theother of said rates, a first manually operable controller for shiftingsaid reverser valve means, a second man ually operable controller forshifting said selector valve means, said first and second controllersbeing selectively operable either for mdependem or for substantiallysimultaneous operation,

and a third controller including dog controlled I means invariablyeffective for shifting said reverser and for substantiallysimultaneously shifting said selector means to the position effectingthe quick traverse rate connection of said source and motor.

13. In a machine tool, the combination of a tool support and a worksupport, a reversibly operable motor connected for movement of saidsupports, a pressure fluid supply source connectible for actuation ofsaid motor alternatively at feed or quick traverse rates, a shiftablereverser means operative to change the direction of said motor movement,a selector means shiftable to eifect said relative movementalternatively at the one or the other of said rates, a first controllerfor shifting-said reverser means, a second controller for shifting saidselector means, each of said controllers including both manuallyoperable and dog operable elements each adapted for independentoperation of the controller, and dog controlled means for shifting saidreverser means from the one to the other direction position thereof andsubstantially simultaneously to dependently shift said selector means tothe position eficting said motor movement at said quick traverse rate.

14. In a machine tool, the combination of a tool support and a worksupport, a reversibly fluid operable motor connected for relativemovement of said supports, a pressure fluid source including a feed ratepump and a quick traverse rate pump and connectible for actuation ofsaid motor at either of said rates, valve means shiftable to eflectmotor movement in either direc-- tion at either of said rates and tointerrupt motor movement, a first dog controlled means for alternativelyand independently effecting a motor interrupting position or a changefrom the one to the other of said rates, and a second dog controlledmeans for effecting a change in motor direction and substantiallysimultaneously effecting a change from the one to the other of saidrates. I

15. In a machine tool the combination of a tool support, a relativelymovable work support, a transmission for said relative movement atalternative feed or quick traverse rates including shiftable reversermeans and shiftable rate selector means, a plurality of independentlyoperable controllers respectively for shifting said reverser means andselector means, power operable shifter means for said reverser means, apower source, shiftable control means'normally connecting said sourceand shifter means to yieldably retain said reverser means in theposition effected by said reverser controller, and dog controlled meansoperative to shift said control means prior to the shifting of saidreverser contrailer and ata predetermined point in support movement toefiect a source and shifter means connecting said source and shiftermeans to yieldably retain said reverser means in the position selectedby said controller, and dog controlled means operative to shift saidcontrol means prior to the shifting of said reverser controller and at apredetermined point in support movement to effect a source and shiftermeans connection for subsequently simultaneously shifting said reversermeans and reverser controller to a position efie'cting opposite supportmovement.

17. In a machine tool the combination of a tool support and a relativelymovable work support, a transmission for said relative movement atalternative feed or quick traverse rates including shiftablereverser'means and shiftable rate selector means, a plurality ofindependently operable controllers respectively for shifting saidreverser means and selector means, fluid operable shifter means for saidreverser means, a pressure fluid source, shiftable valve means normallyconnecting said source and shifter means to yieldably retain saidreverser means in the position effected by said reverser controller, anddog controlled means operative to shift said valve means prior to theshifting of said reverser controller and at a predetermined point insupport movement to effect a source and shifter means'connection forsubsequently shifting said reverser means and reverser controller to aposition effecting opposite support movement.

18. In a machine tool, the combination of a tool support, a relativelymovable work support, a

to a position effecting opposite support movement.

, 19. In a machine tool the combination of. a tool support, a relativelymovable work support, a transmission for said relative movement atalternative feed or quick traverse rates including shiftable reversermeans and shiftable rate selector means, a plurality of independentlyoperable controllers respectively for shifting said reverser means andselector means, power operable shifter means for said reverser means,power operable shifter means for said selector means, a power source,shiftable control means normally connecting said source and reversershifter means to yieldably retain said reverser means in the positioneffected by said reverser controller, and dog controlled means operativeto shift said control means at a predetermined point in said supportmovement to effect a connection of said source and shifters for shiftingsaid reverser means to a position effecting opposite support movementand for dependently substantially simultaneously shifting said selectormeans to a position efl'ecting said quick traverse rate.

20. In a machine tool the combination of a tool support and a relativelymovable work support, a transmission for said relative movementincluding a. fluid operable motor and pump means for de ve y of fluid tosaid motor at alternative feed or quick traverse rates, reverser meansshiftable for changing the direction of actuation of said motor,selector means'shiftable for effecting the one or the other of saidrates of fluid delivery to said motor, a plurality of independentlyoperable controllers respectively for shifting said reverser means andsaid selector means, a fluid operable shifter means for said reversermeans, fluid operable shifter means for said selector means, a pressurefluid source, valve means shiftable for controlling the connection ofsaid source and shifters, means normally positioning said valve means toconnect said source and reverser shifter means to yieldably retain saidreverser means in the position effected by said reverser controller, anddog controlled means operative to shift said valve means at apredetermined point in said support movement to efiect connection ofsaid source and shifters for shifting said reverser means to a positioneffecting the opposite support movement and for dependentlysubstantially simultaneously shifting said selector means to a positioneffecting said quick traverse rate.

21. In a machine tool the combination of a tool support and a relativelymovable work support, a transmission for said relative movementincluding a fluid operable motor and pump means for delivery of fluid tosaid motor at alternative feed or quick traverse rates, reverser meansshiftable for changing the direction of actuation of said motor,selector means shiftable for effecting the one or the other of saidrates of fluid delivery to said motor, a plurality of independentlyoperable controllers respectively for shifting said reverser means andsaid selector means, a fluid operable shifter means for said reversermeans, a pressure fluid source, shiftable valve means for connection ofsaid source and shifter, means normally positioning said valve means toconnect saidsource and shifter to yieldably retain said reverser meansin the position eifected'by said reverser controller, and dog controlledmeans operative to shift said valve means at a predetermined point insaid support movement to effect a connection of said source and shifterfor shifting said reverser means to a position effecting oppositesupport movement.

22. In a machine tool the combination of a tool support, a relativelymovable work support, a transmission for said relative movementincluding a fluid operable motor and pump means for delivery of fluid tosaid motor, reverser means shiftable for changing the direction of motoractuation, a controller shiftable for shifting said reverser means,fluid operable shifter means for said reverser means, a source ofpressure fluid, valve means shiftable for controlling the connection ofsaid source and shifter means, means normally positioning said valvemeans to yieldably retain said reverser means in theposition effected bysaid controller, and dog controlled means operable to shift said valvemeans at a predetermined point in said support movement to effect aconnection of said source and shifter means for shifting said reversermeans to'a position effecting opposite support movement.

23. In a machine tool the combination of a tool support, a. relativelymovable work support, a transmission for said relative movement atalternative feed or quick traverse rates including shiftable reversermeans and shiftable rate selector means, a plurality of independentlyoperable controllers respectively for shifting said reverser means andselector means, power operable shifter means for said reverser means, apower source, shiftable control means normally connecting said sourceand shifter means to yieldably retain said reverser means in theposition effected .shiftable reverser means and shiftable rate selectormeans, a plurality of independently operable controllers respectivelyfor shifting said reverser means and selector means, a power operableshifter means for said reverser means, a power operable shifter meansfor said selector means, a power source, shiftable control means, meansnormally positioning said control means to connect said source andreverser shifter to yieldably retain said reverser means in the positioneffected by said reverse controller, a positive stop means includingelements abuttable to prevent support movement past a predeterminedpoint in one direction thereof, and power operable means operative toshift said control means at a predetermined interval subsequent to theabutment of said elements to effect a connection of said source andshifters for shifting said reverser means to a position effecting theother direction of support movement and for dependently substantiallysimultaneously shifting said selector means to a position effecting saidquick traverse rate. a

25. In a machine tool the combination of a tool support and a relativelymovable work support, a transmission for said relative movement atalternative feed or quick traverse rates including shiftable reversermeans and shiftable rate selector means, a pluralityof independentlyop-' erable controllers respectively for shifting said reverser meansand selector means, power operable shifter means for said selectormeans, a

power source, shiftable control means, a positive stop means includingelements abuttable to prevent support movement past a predeterminedpoint in one direction thereof, and power means operative to shift saidcontrol means at a predetermined interval subsequent to the abutment ofsaid elements to effect a connection of said source and shifters forshifting said reverser means to a position effecting the other directionof support movement and for dependently substantially simultaneouslyshifting said selector means to a position effecting said quick traverserate.

26. In a inachine tool the combination of a tool support and arelatively movable work support, a transmission for said relativemovement at alternative feed or quick traverse rates including shiftablereverser means and shiftable rate selector means, a pluralityofindependently operable controllers respectively for shifting saidreverser means and selector means, fiuid operable shifter means for saidreverser means, fluid operable shifter means for said selector means, a

source of pressure fiuid,'shiftable control valve,

means, a positive stop means including elements abuttable to preventsupport movement'past a' abutment of said elements to effect aconnection .of said source and shifters for shifting said reverser meansto a position effecting the other direction of support movement and fordependently substantially simultaneously shifting said selector means toa position effecting said quick traverse rate.

27. In a machine tool the combination of a tool support and a relativelymovable work support, a transmission for said relative movementincluding a fluid operable motor and pump means for delivery of fluid tosaid motor at alternative feed or quick traverse rates, reverser meansshiftable for changing the direction of actuation of said motor,selector means shiftable for effecting the one or the other of saidrates of fluid delivery to said motor, a plurality of independentlyoperable controllers respectively for shifting said reverser means andsaid selector means, fluid operable shifter means for said reversermeans, fluid operable shifter means for said selector means, a sourceofpressure fluid, shiftable control valve means, a positive stop meansincluding elements abuttable to prevent support movement past apredetermined point in one direction thereof, and power means operativeto shift said control valve means at a predetermined interval subsequentto the abutment of said elements to effect a connection of said sourceand shifters for shifting said reverser means to a position effectingthe other direction of support movement and for substantiallysimultaneously shifting said selector mean's'to a position effectingsaid quick traverse rate.

' 28. In a milling machine the combination of a rotatable tool spindle,a work support reciprocable in a path transverse to the axis of saidspindle. a transmission for said work support movement includingreverser means shiftable to effect opposite direction positions andselector means shiftable for support movement alternatively at feed orquick traverse rates, a plurality of controllers each independentlyoperable and respectively for shifting said reverser means and saidselector means, power operable shifter means for said reverser means, apower source, shiftable control means normally connecting said sourceand shifter to yieldably retain said reverser means in the positioneffected by said reverser controller, and dog controlled means operativeto shift said control means at a predetermined point in supportmovementto effect a source and shifter means connection for shifting saidreverser means to a position effecting opposite support movement.

29. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a path transverse to the axis of saidspindle, .a transmission for said work support movementincludingreverser means shiftable to effect opposite direction positions andselector means shiftable for support movement alternatively at feed orquick traverse rates, a plurality of controllers each independentlyoperable and respectively for shifting said reverser means and saidselector 'means, fluid operable shifter means for said reverser means, apressure fluid source,

shiftable valve means normally connecting said source and shifter meansto yieldably retain said reverser means in the position effected by saidreverser controller, and dog controlled means operative to shift saidvalve means at a predeterq mined point in support movement to effect asource and shifter means connection for shifting said reverser means toa position effecting opposite support movement.

30. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a path transverse to the axis of saidspindle, a transmission for said work support movement includingreverser means shiftable to effect opposite direction positions andselector means shiftable for support movement alternatively at feed orquick traverse rates, a plurality of controllers each independentlyoperable and respectively for shifting said reverser means and saidselector means, power operable shifter means for said reverser means,power operable shifter means for said selector means, a power source,shiftable control means, a positive stop means including elementsabuttable to prevent support movement past a predetermined point in onedirection thereof, and power means operative to shift said control meansat a predetermined interval subsequent to the abutment of said elementsto effect a connection of said source and shifters for shifting saidreverser means to a position effecting the other direction of sup- Iport movement and for dependently substantially simultaneously shiftingsaid selector means to a position effecting said quick traverse rate.

31. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a path transverse to the axis of saidspindie, a transmission for said work support movement includingreverser means shiftable to effect opposite direction positions andselector means shiftable for support movement alternatively at feed orquick traverse rates, a plurality of controllers each independentlyoperable and. respectively for shifting sa-id reverser means and saidselector means, fluid operable shifter means for said reverser means,fluid operable shifter means for said selector means, a source ofpressure fluid, shiftable control valve means, a positive stop meansincluding elements abuttable to prevent support movement past apredetermined point in one direction thereof, and power means operativeto shift said control valve means at a predetermined interval subsequentto the abutment of said elements to eifect a connection of said sourceand shifters for shifting said reverser means to a position effectingthe other direction of support movement and for substantiallysimultaneously shifting said selector means to a position effecting saidquick traverse rate.

32. In a milling machine the combination of a rotatable tool spindle, awork support reciprocable in a path transverse to the axis of saidspindle, a transmission for said work support movement includingreverser means shiftable to effect opposite direction positions andselector means shiftable for support movement alternatively at feed orquick traverse rates, a plurality of controllers each independentlyoperable and respectively fo shifting said reverser means and saidselector means for said reverser means, power operable shifter means forsaid selector means, a power source, shiftable control means normallyconnecting said source and reverser shifter means to yieldably retainsaid reverser means in the position effected by said reversercontroller, and dog controlled means operative to shift said controlmeans at a predetermined point in said support movement to effect aconnection of said source and shifters for shifting said reverser meansto a position effecting opposite support eans, power operable shiftermovement and for dependently substantially simultaneously shifting saidselector means to a position effecting said quick traverse rate.

33. In a machine tool the combination of a tool support and a relativelymovable work support, a transmission for said relative movementincluding a shiftable reverser means and selector means shiftable foralternative feed or quick traverse rates, a plurality of independentlymanually operable controllers respectively for shifting said reversermeans and selector-means, a plurality of fluid operable shiftersrespectively for said reverser means and selector means, a pressurefluid source, valve means for connection of said source and shiftersincluding a portion normally operative to yieldably retain said reverserin the position selected by said reverser controller and a portion dogoperable to effect the other position of said reverser, said valve meansalso including another portion operable in accordance with the operationof said dog operable portion to connect said source and shifters toshift said selector to a position effecting said quick traverse rate.

34. In a machine tool having a rotatable spindle and a reciprocablesupport, the combination of a spindle transmission including meansshiftable for alternatively establishing or interrupting spindlerotation, a support transmission including a pressure fluid source, a'piston device connected for support movement and channel meansconnectible between said source and piston device, valve meansassociated with said channel means and adjustable for eifecting reversalof support movement and for alternatively effecting a feed rate or arelatively fast' quick traverse rate, a plurality of independentlymanually operable controllers respectively for shifting said shiftablemeans for adjusting said valve means to reverse the direction'of supportmovement and for adjusting said valve means to change from the one tothe other of said rates. and other control means operatively connectiblefor substantially simultaneously shifting said valve means to eifectreversal of said support together with a change of support rate andshifting said shiftable means to effect interruption of said spindlerotation.

35. A machine tool as specified in claim 34 in which said other controlmeans includes means limiting-said support reversal, change of supportrate and shifting of said shiftable means to the order recited.

36. In a machine tool having a rotatable spindle and a'reciprocablesupport, the combination of a spindle transmission including meansshiftable for alternatively establishing or interrupting spindlerotation, a support transmission including a feed rate pump, a quicktraverse rate pump, a piston device connected for support movement andchannel means connectible for operation of said piston device from saidpumps, reverser valve means associated with said channel means andadjustable for effecting reversal of support movement from either ofsaid pumps, rate change valve means associated with said channel meansand adjustable for alternatively connecting said pumps to effect a feedrate or a quick traverse rate of said support, a plurality ofindependently manually operable controllers respectively operative forshifting said shiftable means, for adjusting said reverser valve meansto reverse the direction of support movement and for adjusting said ratechange valve means from the one to the other of said rates, and othercontrol

